Fluid control mechanism for driving winding machines



June 10, 1952 J. H. WHITE 2,599,795

FLUID CONTROL MECHANISM FOR DRIVING WINDING MACHINES Filed Dec. 18, 1948 5 Sheets-Sheet l June 10, 1952 J. H. WHITE 2,599,795

mum CONTROL MECHANISM FOR DRIVING WINDING MACHINES Filed DC. 18, 1948 3 Sheets-Sheet 2 INVENTOR. (7015125216. E m

June 10, 1952 J. H. WHITE 2,599,795

FLUID CONTROL MECHANISM FOR DRIVING WINDING MACHINES Filed Dec. 18, 1948 3 Sheets-Sheet 3 X 77- Pb F $329/Q ll 4 152 w x I I f) I 16 F {I W I l ll 1? 19 [Q :3 30 2 INVEN TOR. I Jbsep 1% We Mznys' Patented June 10, 1952 QUNITED STATES PATE Q V,

FLUID CONTROL MECHANISM FOR DRIVING WINDING MACHINES Joseph H. White, Ashaway, R, I. V Application December 18, 1948, Serial No. 66,059

4 Claims. (01. 74- 778) This invention relates to'a machine which will wind webbed material, such as fabrics, paper, film, or wire from a starting small diameter to a roll or reel of any required diameter.

Inthe use of machines of this character heretofore, the material to be wound has usually been supplied to the machine or winder at a constant speed and some complications have ensued in maintaining the tension at the take-up package uniform, due to the increasing diameter of the package ;as the material is wound thereon. A change of revolutions per minute of the take-up package is necessary and this is usually taken care of by the means of a Slipping belt or disc drive, so'arranged that as the roll increases in diameter, the belt or disc slips more and more. This usually results in a more or less jerky drive because the co-eflicient of friction on the belt surface is never uniform over the whole surface, thus resulting in an uneven torque at the winding shaft. Also, as the take-up roll increases in diameter, it becomes heavier requiring more horsepower to drive it, which is another variable which must be taken into consideration. Usually, an idler or take-up roll riding on the belt is periodically adjusted by the operator tightening the belt more and more as the roll grows larger in diameter."

One of the objects of this invention is to provide a mechanical means for automatically holding the tension on the work the same throughout the operation of the take-up roll.

Another object of this invention is to provide frictionless means which will automatically hold the tension the same throughout the entire roll as the reeling occurs.

Another object of this invention is to provide a mechanical means for accomplishing this uniform tension so that the attention of an operator may be reduced to a minimum.

Another object of this invention is to provide a'finely adjusted control for the tension on the take-up shaft.

Another object of this invention is to provide a machine which will provide a light tension or a tensionless roll of any diameter.

Another object of this invention is to provide a machine which will operate on any load with an adequate dissipation of the heat which is generated.

With these and other objects in view, the invention consists of certain novel features of construction, as will be more fully described and particularly pointed out in they appended claims.

In the accompanying drawings:

Figure, 1 is an elevation showing the winding machine and web material being wound thereby with the invention applied thereto;

Figure 2 is an end View of a fragmental portion of the structure shown in Figure 1;. v

Figure 3 is a section on line 33 of Figure 2;

Figure 4 is a section on line 44 of Figure 1;

Figure5 is a detail sectional view illustrating the differential gearing for the transmission of power;

Figurefi is a sectional viewon line 66 of Figure 5 on a somewhat reduced scale; and

Figure 7 is a diagrammatic view illustrating the power transmission.

In proceeding with this invention, I interpose differential gearing between the drive shaft and the driven shaft, which latter is used for rotating the take-up package. The differential gearing employs a unit which is interposed between the two shafts and which itself is rotatable relative to either of the shafts. I control this unit by causing it to operate a pressure fluid system which may be throttled so as'to vary the load which is applied to the unit, and I als'o'interpose a' mechanical brake which is automatically released as pressure is built up in the fluid system. By this arrangement, the power and speed which is applied to the driven shaft to which the take-upis connected is nicely controlled so that its speed varies with the diameter of the take-up package and maintains a constant tension upon the work. Additionally, in cases where I desire tooperatethe take-up package without applying ;any tension to the work, I provide an additional pressure fluid 'system driven from the driven shaft so that. a retardant will be placed upon the driven shaft as I throttle this second fluid system. In this way, a tension on the work may be nicely controlled,and the work may be wound tensionless by throttling this system to supply the retardant on the driven shaft which would ordinarily be supplied bythe tension of the work itself, or the load which it supplies.

With reference to the drawings, a framework I0 supports a power shaft I I through which power is applied to the machine and is transmitted by gears I2 and I3 which may act as change gears to an auxiliary shaft I4 which in turn transmits its motion by chain I 5 to the driven shaft iii of the differential gear train designated generally I! (see Fig. '7). and housed within a casing I8 iipported on the upper end of the framework 3 The driven shaft of the differential gear train I9 operates the take-up shaft 28, either by being coupled directly thereto or being driven through a chain or some train of gears as may be desired. The take-up roll H is mounted on this take-up shaft 28 and is supported by a standard 22 having a bearing 23 at its upper end, as shown in Figurel. The work or web of material 24 is illustrated in Figure l as being wound upon the take-up roll 2I and is drawn from some suitable supply indicated at 25 supported on roll 26 having trunnions 21 in suitable bearings 28.

' [9 or the take-up roll 20 so that the material 24 may be wound upon the take-up roll without Referring more particularly to Figure ,5, the

drive shaft I5 is rotatably supported in bearings 38 and 3| located in an extension 32 of the easing I8. The hub 33 of a bevel gear 34 is mounted on th inner end of the shaft I5 and is keyed to rotate therewith. The driven shaft I9 is supported in bearing 35 in an extension 36 of the casing I8 and has the hub 31 of a bevel gear 38 keyed thereon. These bevel gears 34 and 38 are connected by a unit designated generally 39 comprising a spider rotatably mounted upon bearings II and 42 on the reduced portion 43 of the driven shaft I9, which latter is supported upon bearing 44 which is located in the bevel gear .34.

Bevel gears 45 and 46 are mounted on the spider 48 and mesh with the bevel gears 34 and 38, these bevel gears being freely rotatable upon the spider and mounted in bearings 41 and 48 at the inner and outer ends of the spider. A spiral gear 58 is mounted on the periphery of the spider in a plane at right angles to the axes of the drive and driven shafts. This spiral gear meshes with the spiral pinion 5| on shaft 52 mounted in bearings 53 and 54 in the casing.

Shaft 52 drives pump 55 through .any suitable driving connection taken from this shaft either directly or by gears or a chain, and this pump operates a pressure fluid system which draws liquid from a reservoir 55 located in the framework I8 by means of a conduit 51 and force the liquid outwardly from the pump through conduit 58, through throttling valve 59, conduits 60 and BI to return to the reservoir 56. The throttling valve is supplied with a dial 62 over which a pointer .63 operates as the handle 64 is turned so as to indicate the setting of the valve for the control of the flow of liquid through the system.

A by-pass 65 is provided with a relief valve 66 therein in order to shunt the liquid past the valve 64, should too great a pressure develop.

A brake I0, shown in greater detail in Figure 4, is applied to shaft 52 on the reduced portion II thereof. The hub I3 is keyed to the shaft II and a block 12 is fixed ontothe casing I8 or the ex tension I4 thereof, which block is recessed as at to receive the drum I3. A brake shoe I6 having a lining "I1 is forced against the drum .13 by means of bolts I8 and springs I9 pressing against the block I2. A cap 80 is fixed to the bolts and is secured to a diaphragm 8| closing a chamber 82 to which fluid through conduit 83 issupplied to release the brake when pressure is built up in the fluid system above described.

A pump 85 (see Figure 1 or Figure 6) is driven fromthe driven shaft or take-up shaft .20 of the differential train by any suitable means such as gears 86, shown in Figure l, or chain 81, shown in Figure 6, and serves to supply pressure in a second pressure fluid system, which fluid is supplied from the reservoir 56in the frame I8 through conduit 88 .to the .pump .85, which discharges through conduit 89 through the throttlingvalve 98 and by Way of conduits 9| and 92 back to the tension.

In operation, the main drive shaft II will be driven in time with the processing unit which is supplying the work to the take-up roll 2|, either by being driven directly from the machine which is doing the processing or by some means operating in time therewith. The brake shoe I6 will be set by the springs I9 against the drum on the driven shaft, so that immediately that the driving shaft of the differential I6 commences to turn, power Will rotate the spider, but slowly, due to the friction brake so that some power will be supplied to the take-up roll and some to the pump 55. As this pump starts circulating the liquid, pressure will be built up so that the diaphragm 8I will operate to release the brake and thereafter, control will be taken over'by the throttle valve 59.

For example, if the input shaft is made to turn three hundred revolutions per minute, and the output shaft is held stationary, the ring gear 50 will turn at one hundred fifty revolutions per minute and in the same direction. The ring gear may drive the spiral gear 5I at a ratio of five to one, and, therefore, the pump shaft 52 will be driven at seven hundred fifty revolutions per minute. If the output shaft is allowedto go free, it will turn at the same speed as the input shaft and in the opposite direction with the gear pump stationary. When the wound material is attached to the output shaft, it will turn at a' speed at which the material will allow it to turn, the tension on the material holding the speed to the required revolutions given at any diameter. the roll increases in diameter, it slows up in revolutions per minute with a, consequent increase in speed at the pump. This acceleration of the pump speed is in direct proportion to the diameter of the batch roll and continues to whatever size the roll is wound. It will, thus, .apl .ar that the pump speed is as follows:

where Je=speed of the pump in revolutions per minute; A=speed of input shaft in R. P..M.; D=speed of output shaft in R. P. M. In this manner, it will be apparent that as the weight of the package increases, additional horsepower will be supplied to turn the package, and that a constant tension will be maintained upon the material so that the uniform winding is provided.

In case it is desired to wind the material tensionless on the shaft, then a retardant to the driven shaft I9 or take-up roll 28 is provided by throttling the secondary pressure system .operated by pump by'the throttle 9,8; In this manner, material may be wound slack upon the takeup package, or with whatever tension maybe desired by operating the control throttle 90.

I claim: 9

l. A- driving mechanism. for a ,take-.up .rol1 comprising a driving shaft, a driven shaft operating said take-up roll, diflerential gearing connecting said shafts including a unit relatively rotatable with reference to both of said shafts, a pressure fluid system including a pump driven from said unit, means for throttling the flow through said system to load said pump and retard said unit, a brake to retard said unit and means responsive to the pressure on said fluid system for releasing said brake.

2. A driving mechanism for a take-up roll as in claim 1 wherein each of said shafts have bevel gears and said unit has a spider with a bevel gear meshing with said shaft bevel gears and in turn carries a gear to drive said pump.

3. A driving mechanism for a take-up roll as in claim 1 wherein said brake is spring actuated to urge said brake into retarding position.

4. A driving mechanism for a take-up roll as in claim 1 wherein said brake is spring actuated to urge said brake into retarding position, and a diaphragm actuated by said pressure opposes said spring and releases said brake.

JOSEPH H. WHITE.

6 REFERENCES CITED The following references are of record in the file of this patent:

5 UNITED STATES PATENTS Number Name Date 1,542,701 Joyner June 16, 1925 1,830,941 I-Iild Nov. 10, 1931 1,957,578 Cook May 8, 1934 10 1,996,815 Kimpton et al Apr. 9, 1935 2,064,295 Crane Dec. 15, 1936 2,276,794 Ricci Mar. 17, 1942 2,372,702 Armentrout Apr. 3, 1945 15 2,523,944 Clary Sept. 26, 1950 FOREIGN PATENTS Number Country Date 716,246 France Dec. 17, 1931 

